Bacon slicer having adjustable control of group size



Jan. 2, 1962 H. G. REICHEL ETAL 3,015,350

BACON SLICER HAVING ADJUSTABLE CONTROL OF GROUP SIZE Filed Oct. 14, 19575 Sheets-Sheet 1 /72MED.6/ E/CHEL 5rspysM/ML/s q INVENTORb an- 2, 1962H. G. REICHEL ETAL 3,015,350

BACON SLICER HAVING ADJUSTABLE CONTROL OF GROUP SIZE Filed Oct. 14, 19575 Sheets-Sheet 2 5751/5. A/ 1/5; INVENTORb H 2 115 By 1 I 47/0/ 2 Jan.2, 1962 H. G. REICHEL ETAL BACON SLICER HAVING ADJUSTABLE CONTROL OFGROUP SIZE Filed Oct. 14, 1957 5 Sheets-Sheet 3 STEP/44M ML /5 I N VENTOR.

Jan. 2, 19 2 H. G. REICHEL ETAL 3,01

BACON SLICER HAVING ADJUSTABLE CONTROL OF GROUP SIZE Filed 001;. 14,1957 5 Sheets-Sheet 4 How/IP06 E/CHEL.

INVENTOR.

BY M

Jan. 2, 1962 REICHEL ETAL 3,015,350

BACON SLICER HAVING ADJUSTABLE CONTROL OF GROUP SIZE Filed Oct. 14, 19575 Sheets-Sheet 5 Q "v Q Q l\ h Q N N R 9. L 5\ 3 O S 6% m 1 \I: V [at mm8: m6 Q 1- 5% r" 3 6; A -'txv'v-v-xnr m r r C r f C Si Han 4P0. 69mm3,615,350 BACON SLICER HAVING ADJUSTABLE CONTROL OF GROUP SIZE Howard G.Reichel and Stephen W. Lis, Chicago, Ill.,

assignors to Swift & Company, Chicago, 111., a corporation of lllinoisFiled Oct. 14, 1957, Ser. No. 689,860 8 Claims. (Cl. 14694) Thisinvention relates in general to improvements in slicing machines and isparticularly directed to a method and device for automaticallyseparating a selected number of slices into a draft while maintaining atleast a minimum established distance between successive drafts.

While the present invention is applicable to numerous types of feedmechanisms it has been found to be particularly suitable for use in abacon slicing machine. This disclosure illustrates such a use; however,it will be obvious that the improvement may be otherwise employedwithout departing from the invention.

In general, bacon slicing machines comprise a horizontal bed, arotatable knife means disposed perpendicular to the bed for slicingmaterial thereon, and a feed carriage movable along the bed at a rightangle to the plane of the knife. The feed carriage is usually actuatedby a hydraulic piston and cylinder and the rate of advance of thecarriage depends upon the amount of fluid introduced into the cylinderto displace the piston. Thus, in prior machines, a iiow valve located inthe hydraulic line leading to the end of the cylinder opposite the feedcarriage has been used to control the rate of feed. Usually, the knifesevers one slice each revolution and it clearly follows that thethickness of each slice will be dependent upon the speed of the knifeand the rate of feed. Preferabl the knife speed is maintained constantduring operation and the slice thickness is controlled by adjusting therate of feed.

An increase in the rate of feed will result in a relative in crease inthe thickness of the slices and may be obtained by increasing the amountof the fluid introduced into the cylinder. However, prior apparatus havelacked eflicient and eifective means to separate or otherwisedistinguish a selected number of slices to form a draft. Presentmarketing techniques dictate that the sliced material be grouped intoconvenient units or drafts for consumer sales. Bacon is normally sold inpackages of shingled slices weighing either one-half pound or one fullpound. Further, it has been found desirable to keep the slice thicknesswithin certain limits. Theoretically the number of slices of a giventhicknes making up a half pound or pound unit may be determined from thephysical characteristics and dimensions of a bacon slab; however, eachslab usually differs somewhat from the others and therefore the weightof individual slices obtained from different slabs may vary. Often thisresults in a change in the number of slices of the given thicknessrequired to make up a draft of the desired weight. The slices, whensevered, fall in shingled fashion onto a continuously moving take-offconveyor. Heretofore slices have been grouped by either momentarilyinterrupting the advance of the feed carriage or momentarilyaccelerating the speed of the take-off conveyor. Both of theseprovisions have had the drawback of being unadaptable to varyingconditions. Prior apparatus have lacked any means to selectively controlthe number of slices per draft and the space between drafts. Further, amomentary interruption has often been insufficient to space the drafts asufiicient distance and has often caused the first and last slices of adraft to differ in thickness from the remaining slices making up thedraft.

It is therefore a principal object of this invention to provide a methodfor automatically grouping bacon slices into drafts of a selected numberof slices.

Another object of this invention is to provide a selec- States Patent Patented Jan. 2, 1962 ice tive means for automatically controlling thenumber of slices making up a draft.

Another object of this invention is to provide a means in a slicingmachine for automatically grouping a draft of a preselected number ofslices.

Still another object of the present invention is to provide an automaticand adjustable means in a slicing machine for stopping the feed for atleast a minimum interval and advancing the feed for a period sufficientto obtain a selected number of slices whereby the slices will be'groupedin a draft of the desired number.

A further object of this invention is to provide an automatic andadjustable means in a slicing machine, having hydraulic means foradvancing a feed carriage toward a knife, to interrupt the flow ofhydraulic fluid for at least a minimum period and allow the flow offluid only during an interval sufiicient to provide a desired number ofslices.

A still further object of this invention is to provide a novel means tocontrol the flow of hydraulic fluid from a hydraulic feed means in aslicing machine and maintain uniform advance of the feed means to obtainslices of a uniform thickness.

Other objects and advantages of the invention will become apparent uponreading the following description taken in conjunction with theaccompanying drawings. One embodiment of the invention hasbeen'illustrated, but

7 it is to be expressly understood that said drawings are for purposesof illustration only and are not to be taken'as a definition of thelimits of the invention, reference being had tothe appended claims forthis purpose. In said drawings:

FIGURE 1 is a perspective view of one form of slicing machine embodyingthe present invention;

FIGURE 2 is a diagrammatic view, in perspective, showing therelationship of the working parts of the slicing machine of FIGURE 1,the hydraulic system and the control device;

FIGURE 3 is a side elevation view of the control device, as seen fromthe position of the knife, showing the index shaft, the cam assembliesand electric switches;

FIGURE 4 is a front elevation of the control device of FIGURE 3 showingthe index plate and the index shaft handle;

FIGURE 5 is a perspective view of the control device shown in FIGURE 4showing the gear reducer;

FIGURE 6 is a partial section view taken at line 66 of FIGURE 3 showingthe relative positions of the cam projections and switches in onechannel of the control device;

FIGURE 7 is a schematic wiring diagram of the control circuit connectingthe valve solenoid and the control device.

Generally the present invention comprises a method for advancing thematerial to be sliced into the slicing means only during certainperiods, interrupting the advance of the material at the end of eachperiod of advancement for an interval of time at least sufficient forthe slices, which were severed, to be acted upon so that they may bereadily distinguished from succeeding groups of slices; and then againadvancing the material into the slicing means. The periods ofadvancement may be regulated to provide for a selection in the number ofslices which may be obtained therein. The apparatus which has beendevised for automatically carrying out the method includes a flowcontrol valve placed in the hydraulic line which normally carrieshydraulic fluid leaving the hydraulic cylinder. This valve is operatedto control the rate of advance of the feed carriage. A valve is locatedin the same line between the flow control valve and the hydrauliccylinder and is normally in a first position to direct fluid leaving thecylinder to the flow control valve. An actuating means is provided tomove the s,o s,sso

valve to a second position to block the flow of fluid from the cylinderand thereby interrupt the advance of the feed carriage. Concurrently,the flow control valve is connected to a source of fluid under apressure equal to the pressure of fiuid normally leaving the cylinder.This design provides a constant unceasing flow of fluid at an evenpressure through the control valve with the result that fluid will notsurge from the cylinder when it is reconnected to the flow controlvalve. Thus, the rate of advance of the feed carriage will be uniformthroughout essentially all of each period of advance.

The actuating means to move the valve is connected to a control devicecomprising a cam means which is rotatable at a fraction of the rate ofthe knife. Each full rotation of the cam means represents a certainnumber of revolutions of the knife, and likewise an equal number ofpossible slices. A first and a second sensing means are associated withand actuated by the cam means. The first sensing means is movablethrough a plurality of positions about the periphery of the cam means(the distance between successive positions is equal to the distanceturned by the cam means for each revolution of the slicing machineknife) and is connected to the valve actuating means to cause the latterto place the valve in its second position, blocking the flow of fluidfrom the cylinders and stopping the feed carriage, when the firstsensing means is actuated by the cam means. The second sensing means isconnected to the valve actuating means to cause the latter to move toits first position, allowing fluid to flow from the cylinder and advancethe feed carriage, when the second sensing means is actuated by the cammeans. Thus, the relative positions of the two sensing means withrespect to the cam means will control the duration of the periods thatmaterial will be advanced into the slicing machine knife, and likewisethe periods that the advance of the material will be interrupted.

The slicing machine illustrated in FIGURES 1 and 2 comprises a bedhaving a flat upper surface 11 upon which a bacon slab may be movedtoward a knife 12. Knife 12 is secured to a rotatable shaft 13 which isdriven by means of a belt 14 connecting a pulley 15, secured to theshaft 13, to another pulley 16 on a motor 17. For purposes of safety,knife 12 is substantially enclosed in a guard 18. A precision gearreducer 19 having a ratio of 80 to l is connected to the knife shaft 13by means of a gear thereon (not shown). A control device generally 20 isconnected to the low speed side of the gear reducer 19 in a manner whichwill be later described. Slidably disposed on the upper surface 11 ofbed 10 is a material feed carriage generally 23. This feed carriageconsists of a pusher member 24 having a pusher face 25 suitable forengaging the end of the material to be sliced. Located at the end of bed10, opposite the knife 12, is a hydraulic cylinder 26. The forward endof the cylinder (nearer knife 12) and the rear end of the cylinder areconnected to fluid lines 27 and 28 respectively. A piston (not shown) isattached to a rod 29 extending from the forward end of cylinder 26.Piston rod 29 is connected to the pusher member 24 and will urge it, andany material forward thereof, toward knife 12 when fluid under pressureis introduced through fluid line 28 to the rear of cylinder 26.

The slicing machine also includes a take-off conveyor generally 32consisting of a plurality of ribbons 33 trained about a pair of drums34, 35 which are rotatably secured to a suitable stand 36. The take-01fconveyor 32 may be driven in any convenient fashion, such as by means ofa separate electric motor, or by suitable connection to motor 17 or toknife shaft 13.

The components of the control device generally 20 are situated in aframe which is secured to the slicing machine above bed 10 proximate tothe knife shaft 13. As seen in FIGURES 3 and 5, an index shaft 41 isrotatably supported between a vertical frame member 42 near one end ofthe frame 40, and an index plate 43 at the opposite end of frame 40. Acrank arm 44 is fastened to the end of the index shaft 41 extending fromthe face of the index plate 43. As illustrated in FIGURE 4, the crankarm 44 is attached to the index shaft 41 by means of a collar 45 formed,in one end of the crank arm 44, concentric about the index shaft 41, anda set screw 46 threaded therein. At the end the crank arm 44 oppositecollar 45 is a handle generally 47. A knurled knob 48 having a threadedinternal passage therein is rotatably secured to the handle 47. Disposedwithin the threaded passage of knob 48 is a threaded locking pin 49,which will be advanced toward the index plate 43 when knob 48 is turnedin a clock-wise direction. In like manner, the locking pin 49 will bewithdrawn when the knob is turned in a counter clock-wise direction. Aplurality of pin seats 50 are located across the face of index plate 43to receive the locking pin 49 and thereby secure the crank arm 44 andindex shaft 41 in any selected position.

As will become clear in the following description the control device 20contains three separate operating channels comprising similar elements.These channels have been designated by the letters A, B, and C andreference characters denoting similar elements in the various channelsbear the appropriate letter as a subscript. Each channel provides ameans for selecting a certain range of number of slices per draft. Theposition of the index shaft 41, as determined by the pin seat 50 inwhich locking pin 49 is secured, controls both the selection of theappropriate channel and the selection of the number of slices to beobtained thereby. In the embodiment described channel A controls theoperation of the feed carriage 23 for from eight to twenty-four slicesper draft; and channels B and C control its operations for fromtwenty-two to twenty-eight and from twenty-nine to thirty-six slices perdraft respectively. It may be seen that since twenty-two to twenty-fourslices per draft may be obtained by employing either channel A or Bthese numbers appear twice on the index plate 43. Also, the amount thatindex shaft 41 must be rotated for each increment of increase in thenumber of slices selected varies somewhat for each of the threechannels. Thus, the distance between pin seats 50 is different in so faras the different channels are compared.

Referring to FIGURES 3 and 5, a pair of vertical frame members 52 and 53are located between the index plate 43 and the frame member 42 in amanner which physically separates the elements of the three channels A,B, and C. The index shaft 41 extends through the vertical frame members42, 52, and 53 and is journaled therein. Only the parts forming channelA will be described in detail since the description will also apply tochannels B and C.

As may be seen in FIGURE 5, a cam assembly generally 55a is situated onthe index shaft 41 between the index plate 43 and the vertical framemember 52. Cam assembly 55a comprises a sleeve 56a, having an innerdiameter slightly greater than the outer diameter of index shaft 41, andfreely rotatable thereon. Adjustably secured to the ends of thesleeve'56a are a pair of cams 57a and 58a. Each of the cams have agenerally circular profile with a single projection covering only asmall portion of its circumference. A gear 59a is fixed concentricallyto the sleeve 56a between cams 57a and 58a. For purposes which willlater become clear, gear 59a has forty-five teeth, while gears 59b and59c have fifty-one and forty-two teeth respectively. As illustrated inFIGURE 3, cam assembly 55a is spaced from theindex plate 43 by a spacerbearing 61 which is secured to the index shaft 41 by means of a setscrew. A similar spacer bearing 62a is secured to the index shaft 41adjacent the opposite end of the cam assembly 55a to preventdisplacement of the cam assembly in the direction of the frame member52.

Immediately adjacent the spacer bearing 62a opposite the cam assembly55a is an arm 64a. Arm 64a extends radially from the index shaft 41 andis attached thereto by means-of collar 65a and set screw. 66a. Anelectric switch 68a is secured to the frame 45 at the rear side of indexplate 43. (Similar switches 68b and 68c are fixed to vertical framemembers 52 and 53 respectively.) Another electric switch 69a is securedto arm 64a and is movable therewith. As illustrated, the switches 68aand 69a are bolted to their supports and are situated radially in linewith cams 57a and 58a respectively. Switch 68a is provided with a triplever 70a having a roller follower 71a. Switch 69a likewise has a triplever 72a and roller follower 73a. Roller followers 71a and 73a ride onthe cams 57a and 58a, respectively, whereby switches 68a and 69a will beactuated briefly by the projections thereon. 1n the preferredembodiment, switch 68a (and switches 63b and 680) is a single polesingle throw type spring loaded to the closed position. Switch 69a (andswitches 69!) and 690) is a single pole single throw type switch springloaded to the open position.

As may be seen in FIGURES 3 and 5, a pair of switching cams 75, 76 arefixed to the left end of index shaft 41 to rotate therewith. Cam 75 hasa raised peripheral portion extending about its circumference a distancerepresenting the angle through'which index shaft 41 may be turned whenselecting a number of slices per draft on channel A. Similarly, cam 76has a raised periphery representing the angle turned by the index shaft41 when selecting drafts on channel B. A pair of single pole, doublethrow, spring loaded electric switches 77, 78 are secured to verticalframe member 42 directly above the earns 75, 76 respectively. Switch 78includes a trip lever 79 and a roller follower 80, thereon, which rideson the peripheral surface of cam 76. Also, switch 77 includes a triplever 81 and a roller follower 82 which rides on cam 75. The switches77, 78 and cams 75, 76 are situated about index shaft 41 so that whenthe shaft 41 is in any position representing channel A the raisedportion of cam 75 holds switch 77 in its first position, and cam 76allows switch 78 to dwell in its first position. When shaft 41 is in anyposition representing channel B cam 75 allows switch 77 to dwell in itssecond position, and the raised portion of cam 76 holds switch 78 in itssecond position. When the index shaft 41 is in a position representingchannel C, switch 77 dwells in its second position and switch 78 dwellsin its first position.

it was indicated that the control device generally 20 is driven from thegear reducer 19. For this purpose a drive shaft 85 (seen in FIGURE 5) isjournaled in frame 4% so that it is spaced from and parallel to theindex shaft 41. One end of the drive shaft 85 is coupled to the lowspeed end of gear reducer 19. Three drive gears 86a, 86b, and 860 arefixed to the shaft 85 at positions directly opposite gears 59a, 59b, and59c (on cam assemblies 55a, 55b, and 550) respectively. Gears 86a and8612 have one hundred twenty teeth and gear 86c has eighty teeth. Threeidler gears 87a, 87b, and 87c are positioned between the opposing gears59 and 86 on the cam assemblies 55 and the drive shaft 85 respectively.The number of the teeth on the idler gears 87 is not important so longas the connected gears properly mesh.

A drive train may be traced for each cam assembly 55 to determine thenumber of revolutions of the knife shaft 13 which is necessary to turnthe cam assembly 55 one complete revolution. It follows that a simpleequation may be developed for such a determination. Where X is thenumber of revolutions of knife shaft 13, N

is the number of teeth on gear 59 and N is the number of teeth on gear86: X=N /N (since 80:1 is the ratio of gear reducer 19). Therefore,considering channel A (cam assembly 55a): X,,=80(45)/120:30. In otherwords, cam assembly 55a rotates once for every thirty revolutions ofknife 12. Similarly, it may be seen that thirty-four revolutions ofknife 12 are required for each full revolution of cam assembly 55b; andforty-two revolutions of knife 12 are required for each revolution ofcam assembly 55c. In practice itwas determined that if feed carriage 23was stopped during a minimum of six revolutions of knife 12, asufiicient space would be obtained between successive drafts. Therefore,the practical maximum limit of the number of slices to be controlled byeach of the channels A, B, and C is six less than the number ofrevolutions of knife 12 representing one complete revolution of camassemblies 55a, 55b, and 550 respectively. As previously indicated,these maximum practical limits are, therefore, twenty-four, twentyeight,and thirty-six slices respectively. Furthermore, as a practical matter,drafts of less than eight slices are seldom, if ever, required;therefore, eight slices was established as the lower working limit ofchannel A. It should be obvious from the foregoing description that whenthe index shaft 41 is positioned to obtain drafts of a selected numberof slices, the space between successive drafts will be dependent uponthe quantity X-S (where S is the number of slices). For example, ifeight slices per draft are required, the distance between drafts will bedependent upon:

or, twenty-two revolutions of knife 12 (the actual distance betweendrafts will equal the distance take-off conveyor 32 travels while knife12 revolves twenty-two times). Also, it was found to be of advantage toprovide for obtaining twenty-two to twenty-four slices on both channelsA and B. In this way, the operator is provided with a means to obtaingreater distance between drafts of that number of slices with only aslight sacrifice in efliciency of operation.

It is preferred to have the advance of feed carriage 23 commence withthe actuation of a switch 68 by the projection on cam 57. Also, theadvance is to be stopped when a switch 69 (which is adjustable by movingindex shaft 41) is actuated by the projection on cam 58. Therefore, itis necessary that from the instant switch 69 is actuated until theinstant that switch 68 is actuated, the cam assembly should turn only anamount representing X S revolutions of knife 12. The angulardisplacement between the projections on cams 57 and 58, and between theswitches 68 and 69 are interdependent. FlGURE 6 graphically illustratesthis relationship and indicates the method by which the initialpositions of the cams and switches about the index shaft 41 may bedetermined. Referring to FIGURE 6, the relationship may be expressed as:

Where E is the angle between a plane containing the axis of index shaft41 and a line connecting that axis and the point on the projection ofcam 58 where switch 69 will be actuated, and a plane containing the axisof index shaft 41 and a line connecting that axis and the point on theprojection of cam 57 where switch 68 will be actuated (measured in unitsof revolutions of knife 12);

X is the number of revolutions of knife 12 representing one revolutionof the cam assembly 55;

S is the number of slices per draft selected; and

D is the angle between the center lines of switches 68 and 69, when theindex shaft has been positioned for S number of slices per draft,measured in units of revolutions of knife 12 (D is a positive value whenmeasured clockwise from switch 68 and a negative value when measuredcounter-clockwise from switch 68).

To illustrate, assume that the control device 20 has been set up fordrafts of eight slices (S=8) and the angular distance between cams 58aand 57a is (Since for channel A, X :30, it may be seen that incrementsof 12 equal the angle cam assembly 55a turns for each revolua negativepole of the source of electric power 91.

H a 7 tion of knife 12; therefore, E=15.) By transposing the formula andsubstituting to find D:

Since D is a positive value, arm 64a must be positioned on index shaft41 so that switch 69a is positioned seven increments (84) clockwise fromswitch 68a. Thus, after switch 69a is actuated to stop the advance ofthe feed carriage 23, cam assembly 55a will turn D and E increments (or22 revolutions of knife 12) before switch 68a will be actuated to startthe advance of the feed carriage and produce the next draft of eightslices. Further the angular displacement between successive pin seats50, indicating the number of slices available on any channel, must beequal to the increment of revolution of the appropriate cam assembly 55representing one revolution of knife 12. In FIGURE 6, D is the anglebetween switches 68a and 69a when the index shaft 41 has been reset for,say, twenty-two slices. Obviously, the shaft 41 will have been turnedthrough fourteen increments counter-clockwise from the eight slicesposition. Therefore, switch 69a will be seven incrementscounterclockwise from switch 68a. It follows that D =-7 and the equationmay be checked by substituting values:

The electrical circuit Referring to the Wiring diagram of FIGURE 7, wire90 connects switch 77 with the positive pole of a source of electricpower 91. A fuse 92 is placed along wire 90. The second position contactof switch 77 is connected to switch 78 by a wire 93. The first positioncontact of switch 77 is connected to the switch 68a by a wire 94a. Wires94b and 940 connect the second position and first position contacts,respectively, of switch 78 to switches 68!: and 68c respectively. Sincethe electric circuits for channels B and C are similar to that forchannel A, only the latter will be described in detail. The pole ofswitch 68a is connected by means of wire 95a to a switch 69a and to theblade terminal of a single pole relay switch 96a. Another Wire 97a isconnected between switch 69a and the upper lead of a solenoid 98a. Thelower lead of solenoid 98a is connected to a common wire 100 which isconnected, through a fuse 101, to the (The lower leads of solenoids 98band 980 are also connected, in parallel, to wire 100.) Another wire 102is connected between the fixed contact points of relay switches 96a,96b, and 960, and one terminal of a valve actuating solenoid 103. Theremaining terminal of valve solenoid 103 is connected to the negativepole of the source of electric power 91 by a Wire 104. Also, a wire10511 is connected between the upper lead of solenoid 98a and thestationary contact of relay switch 96a.

Thus, the path of electric current may be traced where the controldevice 20 is set for, say, eight slices per draft. As may be followed inFIGURE 7, electric current will flow along wire 90 from the source 91 toswitch 77. Where eight slices have been selected, cam 75 holds switch 77to direct current to channel A by way of wire 94a to switch 68a. Switch68a is normally closed and is only momentarily opened by the cam 57aonce each revolution of cam assembly 55a. From switch 68a electriccurrent 'is directed to both the relay switch 96a and the switch 69a(which is normally open) along wire 95a. When closed, switch 69a passescurrent along Wire 97a to the solenoid 98a which is connected directlyto a return wire 100 to the source of electric power 91. Relay switch96a Will be closed when the solenoid 98a is so energized and cunent willpass from switch 68a along wire 95a through relay switch 96a to wire 102and the valve solenoid 103. As will be later made clear, energization ofthe valve solenoid 103 will stop the feed carriage 23. This occurs whenswitch 69a is momentarily closed by cam 58a. Since switch 69a isimmediately opened again the solenoid 98a would normally be de-energizedand relay switch 96a would spring open to break the circuit to valvesolenoid 103. However, wire 105a will carry current from the fixedcontact of relay switch 96a back to the solenoid 98a when the relay isclosed. Therefore, once the relay switch 96a is closed, current willflow from switch 68a directly to the solenoid 98a, and the opening ofswitch 69a will not break the connection so long as switch 68a remainsclosed. Next, cam 57a momentarily opens switch 68a to begin a new feedsequence. When the switch 68a is opened, current cannot pass to eitherthe relay switch 96a or to switch 69a. Thus, solenoid 98a will bede-energized and will not again close relay switch 96a until both switch69a and 68a are in a closed position at the same instant. When relayswitch 960! is opened current will not pass through valve solenoid 103and the feed carriage will advance toward knife 12.

As may be seen in FIGURE 7, when the index shaft 41 is turned to aposition for drafts of a number of slices controlled by either channel Bor C cam 75 will allow switch 77 to dwell in its second position whichplaces wire 93 to switch 78, in communication with the electric powersource 91, and disconnects wire 94a (to channel A). The position ofindex shaft 41 also controls cam 76 which moves switch 78 to place wire94b (channel B) or wire 94c (channel C) in electrical communication withwire 93. Thus, the appropriate channel circuit will be placed betweenthe source of electric power 91 and the valve solenoid 103 when theindex shaft is positioned by turning crank arm 44 and securing thelocking pin 49 in any of the pin seats 50. Preferably, the index shaft41 is formed with a hollow center and the wires to the switches 69a,69b, 690, on arms 64a, 64b, and 640, respectively, are placed therein.Wires to switches 68a, 68b, and 68c, and switches 77, 78 are attached tothe frame 40 of the control device 20.

The hydraulic circuit Referring to FIGURE 2, the valve solenoid 103 isconnected to a four-way valve 108 which has two operating positions.Normally, valve 108 is spring loaded to a first position when solenoid103 is not energized. When the solenoid 103 is energized valve 108 willbe forced to a second position. Fluid line 27 is connected to one portof the four-way valve 108. A fluid line 109 is connected between asecond port in four-way valve 108 and a flow control valve 110. The flowcontrol valve 110 maintains fluid line 109 in communication with a fluidline 111, attached thereto, which empties into a reservoir or sump 112.Flow control valve 110 is adjustable manually to vary the rate at whichfluid may pass from line 109 to the sump 112 by means of a dial 113(shown in FIG- URE 1). When the feed carriage is advancing hydraulicfluid will be forced from the forward end of cylinder 26 through line 27and the valve 108 (in its first position) to'line 109. Thence, the fluidpasses through flow control valve 110 (by means of which the rate ofadvance of the feed carriage 23 is regulated) to the sump 112 by way ofline 111.

Another fluid line 115 is attached to a third port on the four-way valve108 connecting it to a pressure reducing valve 116. The pressurereducing valve 116 in turn is connected to'a pressure regulator 117 of acentrifugal pump 118 by fluid line 119. A fluid line 120 carrieshydraulic fluid from the sump 112 to the inlet port of pump 118, and aline 121 discharges fluid from the pressure regulator 117 back to thesump 112. The pump 118 is driven by an electric motor 123 coupledthereto. In some installations it may be possible to drive the pump 118by connecting it to the knife motor 17. Pump 118 and pressure regulator117 are set to deliver hydraulic fluid to the pressure reducing valve116 at a pressure equal to the pressure of fluid normally leavingcylinder 26 through line 27.

Under usual operating conditions when the feed carriage 23 is beingadvanced the forces acting on the two sides or" the piston in cylinder26 are nearly balanced. Since the area of the piston on the endconnected to piston rod 29 is less than the area of its free end, it isclear that the fluid pressure in the forward end of cylinder 26 (and inline 27) will be somewhat greater than the pressure in the rear end ofthe cylinder. In the actual machine it was found that when hydraulicfluid was introduced to the rear end of cylinder 26 at 150 p.s.i. thepressure of the fluid leaving the forward end of the cylinder wasapproximately 250 p.s.i. Therefore, the pump 118 and pressure regulator117 are set to deliver hydraulic fluid at 250 p.s.i. to the pressurereducing valve 116. The fluid introduced to line 115 is also at 250p.s.i. When the valve solenoid 103 is energized, the four-way valve 108is moved to its second position, which blocks 'line 27 and places line115 in communication with line 109, and fluid from the reducing valve116 is directed to the flow control valve 111 Thus, fluid at 250 p.s.i.will normally continuously pass through the flow control valveregardless of the position of four-Way valve 188. At the time that thefourway valve 108 is again moved to its first position, and fluid passesfrom the forward end of cylinder 26 through the flow control valve 110,all of the hydraulic components will contain fluid at about the normaloperating pressures. Thus, there will be no tendency for the piston tosurge forward at the beginning of a feed cycle.

Another fluid line 125 connects the low pressure end of the pressurereducing valve 116 to a two-way valve 126. The pressure reducer 116directs fluid at 150 p.s.i. into this line. A manual selector handle 127is connected to the valve 126 and provides a means for an operator tostop the feed carriage at any time. When the handle 127 is pulledoutwardly the valve is placed in its first position directing hydraulicfluid from line 125 to a line 128. When the handle 127 is pushedinwardly valve 126 is placed in its second position which connects line128 to a line 129 to the sump 112, and at the same time connects fluidline 125 to a line 130. Line 130 is connected to another fluid line 131at the flow control valve 110 and empties into the sump 112. When thetwo-way valve 126 is placed in its second position, the 150 p.s.i. fluidfrom the pressure reducer valve 116 will be returned to the sump 112 andfeed carriage 23 will stop. However, when valve 126 is placed in itsfirst position, the fluid at 150 p.s.i. will be directed through line128 to a reversing valve 132. This reversing valve 132 is a four-wayvalve having three operative position. Valve 132 is provided with both amanual control handle 133 and a hydraulic actuator 134. Reversing valve132 is spring loaded to a first or normal position which connects fluid128 to line 28 and the rear of cylinder 26. When both valve 126 andvalve 132 are in their first positions, hydraulic fluid at 150 p.s.i.will be introduced to the rear end of cylinder 26. Assuming at this timethat valve 103 is in its first position (directing fluid from theforward end of cylinder 26 through the flow control valve 110), the feedcarriage 23 will be advanced when fluid at 150 p.s.i. is introduced tothe rear end of the cylinder.

A fluid line 137 connects the reversing valve 132 with line 27 through aT connector 138. Reversing valve 132 is also connected to the sump 112by a fluid line 139. Holding the control handle 133 inwardly places thereversing valve in its second position connecting line 128 to line 28and connecting line 137 to line 139. Thus, when valve 132 is in thesecond position, fluid at 150 p.s.i. will be directed to the rear ofcylinder 26 and an unimpeded passage is connected between the forwardend of the cylinder and sump 112. This connection provides a means toquickly advance the feed carriage at any time an operator elects to doso. When the control handle 133 is held outwardly, the reversing valve132 is placed in its third position connecting line 28 to line 139 andconnecting line 137 to line 128. In this manner, hydraulic fluid at 150p.s.i. is introduced to line 27 and the forward end of cylinder 26 whilethe rear end of the cylinder is connected directly to the sump 112. Theeffect is to quickly reverse the motion of the piston in cylinder 26 andmove the feed carriage 23 away from knife 12.

Valve 132 may also be placed in the third or reversing positionautomatically by the hydraulic actuator 134. As may be seen in FIGURE 2,the hydraulic actuator 134 is connected to a rotary pilot valve 141 by afllld line 142. The pilot valve 141 is in turn connected to a Tconnector 143 in line 128 by a fluid line 144. Thus, the pilot valve 141may direct hydraulic fluid at 150 p.s.i. to the actuator 134 when valve126 is in its first position. Fluid line 145 connects the pilot valve141 to the sump 112. Since it is desirable to automati Cally reverse thefeed carriage 23 when it reaches the end of a feed stroke, suitablemechanical linkages are pro-. vided to actuate the pilot valve 141. Arod 147 is slidably secured beneath the upper surface 11 of bed 10 andextends for a length equal to the maximum feed stroke of the carriage23. A lug 148 is connected to the end of rod 147 near knife 12 andprojects into the path of the pusher member 24. Another lug 149 isconnected to the opposite end of rod 147 and also extends into the pathof the pusher member 24. One end of a lever 151 is pivotally connectedto the rod 147. The other end of lever 150 is pivotally connected to anactuator handle 151 of pilot valve 141. The lever 159 is pivoted about apin 152 so that a small movement of the rod 147 will fully actuate thepilot valve 141. When the feed carriage 23 reaches the end of itsforward movement, the pusher member 24 will strike lug 148 and slide rod147 slightly forward. Lever 150 is pivoted thereby and the pilot valveis turned to direct fluid at 150 p.s.i. to the hydraulic actuator 134.The reversing valve 132 is placed in its third position, thereby, andthe feed carriage 23 will be reversed. When the carriage 23 moves to itsrear-most position, the pusher member 24 will strike lug 149, and slidebar 147 rearwardly to pivot lever 150 and move the pilot valve 141 toconnect the hydraulic actuator 134 to line 145 and sump 112. Thereversing valve 132 will spring back to its first or normal position,which directs fluid to line 28 and the rear of cylinder 26, whenpressure is released in the actuator 134 and therefore the carriage willautomatically move forward toward knife 12.

Operation The operation of the slicing machine should be apparent fromthe foregoing description. The slicing knife 12 and the hydraulic pump118 are started by connecting the motors 17 and 123 with a suitablesource of electric power (not shown). Valve 126 is placed in its firstposition and the reversing valve is held in its third position to movethe feed carriage 23 rearwardly, until the carriage reaches the end ofits path. At this time, the reversing valve 132 is released (springingto its first position) and valve 126 is placed in its second position,thus stopping flow of hydraulic fluid to cylinder 26 and thereforestopping the feed carriage 23. A bacon slab is then placed upon the bed113 between the pusher member 24 and the knife 12, and the controldevice generally 21 is set for the desired number of slices per draft.To do this, crank arm 44 is rotated until the locking pin 49 may bescrewed down into the appropriate pin seat 56. At the same time the dial113 on the flow control valve 111 is adjusted to regulate the properslicethickness. Valve 126 is then returned to its first position tostart the feeding operation, and the reversing valve 132 is held in itssecond position to quickly advance the feed carriage 23 until the pusherface engages the bacon slab and advances it to the knife 12. Thereversing valve 132 is then released allowing it to spring to its firstor normal position for normal forward feed. At this time the slicingmachine will operate automatically. If at any time it is necessary tostop the advance of the feed carriage 23, valve 126 is placed in itssecond position. Or if it is. desirable to reverse the carriage 23, thereversing valve 132 is held in its third position.

The cam assemblies 55 will rotate continuously while knife shaft 13 isrotating. During automatic operation when a projection on cam 58 (in theenergized channel) actuates switch 69 (movable with index shaft 41) anelectric circuit is completed to the valve solenoid 163. The valvesolenoid is thereby energized and moves the fourway valve 168 from itsfirst to its second position. This position of the valve 198 preventsfluid from leaving the forward end of the cylinder 26 and thus, the feedcarriage will stop. At the same time, the flow control valve 110 isconnected to a supply of hydraulic fluid at about 250 psi. The camassembly 55 continues to rotate, and when cam 57 actuates switch 68 theelectric circuit to the valve solenoid 103 will be broken. The valvesolenoid 103 is then de-energized and valve 1% will return to its firstposition. This re-connects the forward end of the cylinder 26 to theflow control valve 110 and fluid will pass therethrough to the sump1112. Feed carriage 23 will advance toward knife 12 until the cam 58again actuates switch 69 and the cycle repeats.

When the feed carriage 23 advances it forces the bacon siab into thepath of the blade of knife 12 to sever slices therefrom. These slices'fall onto the ribbons 33 of the continuously moving take-off conveyor32 in a shingled fashion. Interruption of the advance of feed carriage23 does not effect the take-off conveyor 32; however, no slices willfall thereon during the interval that the carriage 23 is stopped. Thus,a space will be left on the take-01f conveyor 32 between the last slicesevered during one cycle and the first slice severed upon commencementof the next succeeding cycle.

This automatic operation will continue until the last of the slab issevered and the feed carriage 23 trips the lug 148. The reversing valve132 will be automatically placed in its third position and the feedcarriage 23 will be drawn rearwardly until it trips lug 149. During thisperiod the next bacon slab is readied and when the carriage has moved tothe rear a sufiicient distance it is placed between the pusher face 25and the knife 12. When lug 149 is tripped the reversing valve 132 willspring to its first position and the feed carriage will start toadadvance toward knife 12 under automatic control. If necessary, valve132 may be operated to quickly advance the carriage and take up anyexcess space between the pusher face 25, the slab, and knife 12. Thecrank arm 44 of the control device 20 and the flow control valve 110 maybe re-positioned for drafts of a different number of slices or slices ofa different thickness at any time during the operation of the machine.

Obviously, many modifications and variations of the invention ashereinbefore set forth may be made without departing from the spirit andscope thereof, and therefore only such limitations should be imposed asare indicated in the appended claims.

We claim:

1. In a slicing machine, in combination: a rotatable slicing knife; cammeans rotatable at a speed proportionate to the speed of said knife; afirst sensing means adjacent said carn means and engageable therebymomentarily once each revolution of the cam means; a second sensingmeans adjacent said cam means and engageable thereby once eachrevolution of the cam means, said first and said second sensing meansbeing adjustable about said cam means with respect to one another; afeed carriage movable toward the slicing knife; advancing means to movesaid carriage toward'said knife; and con- 12 necting means linking saidfirst and said second sensing means to said advancing means whereby saidcarriage will be moved only during the interval between the time saidcam means engages said second sensing means and the time said cam meansengages said first sensing means.

2. In a slicing machine, in combination; a rotatable slicing knife; afeed carriage disposed for moving material to be sliced toward saidknife; advancing means connected to advance said feed carriage towardsaid knife; slice removing means positioned adjacent said knife oppositesaid feed carriage for receiving slices of material severed by saidknife; drive means connected for rotating said knife at a constantspeed; cam means positioned to be rotated by said drive means at a speedproportionate to the speed of said knife; a first sensing means adjacentsaid cam means engageable thereby momentarily once each revolution ofthe cam means and connected to stop said advancing means, a secondsensing means adjacent said cam means engageable thereby once eachrevolution of the cam means and connected to start said advancing means,said first and said second sensing means being adjustable about said cammeans with respect to one another whereby slices will be severed fromthe material only during the interval between engagement of said secondand said first sensing means by said cam means and the slices will beremoved by said slice removing means a distance suflicient to define agroup during the interval between the engagement of said first and saidsecond sensing means by said cam means.

3. In a slicing machine having a slicing knife adapted to slice materialadvanced by a feed carriage and an advancing means for moving the feedcarriage, the improvement for controlling the advancing means, saidimprovement comprising: a frame; an index plate fastened to one end ofsaid frame; a shaft rota-tably secured within said frame and extendingthrough said plate; handle means secured to said shaft adjacent the faceof said plate for selecting a position of said shaft; cam means freelyrotatable about said shaft; a first sensing means fixed to said shaftadjacent said cam means engageable thereby once each revolution of saidcam means and connected to stop the advancing means; a second sensingmeans fixed to said frame adjacent said cam means engageable therebyonce each revolution of said cam means and connected to start theadvancing means; and means to cause said cam means to rotate whereby thefeed carriage will be advanced toward the knife for a portion of onerevolution of said cam means and will stop for the remainder of therevolution of said cam means according to the position of said shaft.

4. A slicing machine comprising, in combination: a bed for supporting amaterial to be sliced; a rotating knife at one end of the bed; a feedcarriage mounted to move along the bed for advancing the material towardsaid knife; hydraulic means connected to the feed carriage for advancingsaid carriage at a rate dependent upon the rate of hydraulic fluidleaving said means; a flow regulator connected to the hydraulic meansfor controlling the rate of fluid leaving said means; a valveconnected,between the hydraulic means and the flow regulator for fullyinterrupting the flow of fluid from said means; a solenoid connected toclose said valve only when energized; a rotatable member associated withthe knife to make one complete rotation for a certain number ofrevolutions of said knife; a first switch adjacent said member operableto energize the solenoid; a second switch adjacent said member operableto de-energize the solenoid, said first and said second switches beingadjustable with respect to each other; and means on the rotatable memberto operate said first switch and said second switch once per rotation ofsaid member.

5. The apparatus of claim 4 including a source of hydraulic fluid at apressure equal to the pressure of fluid normally flowing through theflow regulator connectable to said regulator by said valve when thevalve is closed.

6. In a slicing machine having a slicing knife and a feed carriagemovable toward the knife, the improvement for advancing the feedcarriage, said improvement comprising: power means connected to movefeed carriage toward the knife, a member rotatable at a speedproportionate to the speed of the knife; a first sensing means adjacentto said member and engageable thereby momentarily once each revolutionof said member; said first sensing means being operatively connected tosaid power means to arrest the movement of the feed carriage; and asecond sensing means adjacent said member and engageable thereby onceeach revolution of said member, said second sensing means operativelyconnected to said power means to initiate movement of the feed carriagetoward the knife whereby the feed carriage will be advanced during theinterval between the time said member engages a second sensing means andthe time said member engages said first sensing means.

7. In a slicing machine, in combination: a rotatable slicing knife; afeed carriage moveable toward the slicing knife; advancing means to movesaid carriage toward said knife; cam means rotatable at a speedproportionate to the speed of said knife; a first sensing mean adjacentsaid cam means and engageable thereby momentarily once each revolutionof the cam means; and a second sensing means adjacent said cam means andengageable thereby once each revolution of the cam means, said first andsaid second sensing means being adjustable about said cam means withrespect to one another, one of said sensing means being connected tostop the advancing means and the other sensing means being connected tostart the advancing means.

8. In a slicing machine having a slicing knife adapted to slice materialadvanced by a feed carriage and an advancing means for moving the feedcarriage, the improvement for controlling the advancing means, saidimprovement comprising: a frame; an index plate fastened to one end ofsaid frame; a shaft rotatably secured within said frame and extending tosaid plate; handle means secured to said shaft adjacent the face of saidplate for selecting a position of said shaft; cam means freely rotatableabout said shaft; a first sensing means fixed to said shaft adjacentsaid cam means engageable thereby once each revolution of said cammeans; a second sensing means fixed to said frame adjacent said cammeans engageable thereby once each revolution of said cam means, one ofsaid sensing mean being connected to stop the advancing means and theother sensing means being connected to start the advancing means; andmeans to cause said cam means to rotate whereby the feed carriage willbe advanced toward the knife for a portion of one revolution of said cammeans and will stop for the remainder of the revolution of said cammeans according to the position of said shaft.

References Cited in the file of this patent UNITED STATES PATENTS2,255,048 Ewald Sept. 9, 1941 2,272,684 Vickers Feb. 10, 1942 2,365,748Curtis Dec. 26, 1944 2,426,835 Mahler Sept. 2, 1947 2,744,553 Folk May8, 1956 2,768,666 Garapolo et a1 Oct. 30, 1956 2,811,997 Schmidt Nov. 5,1957 2,812,792 Allbright Nov. 12, 1957 2,870,810 Folk Jan. 27, 1959UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent, No, 3 Ol535O January 2 1962 Howard G Reichel et alo It is hereby certified thaterror appears in the above numbered patent requiring correction and thatthe said Letters Patent should read as corrected below.

Column 5 line 68,, before N insert 8O column 6 line 72 strike out "up";column line 25 for "D read D column ll line 50 strike out "ad-"'0 Signedand sealed this 1st day of May 1962, I

(SEAL) Attest:

DAVID L. LADD ERNEST W SWIDER Attesting Officer 7 Commissioner ofPatents

